Power transmission



Nov. 8, 1938. R. E'..MlLLlCAN POW ER TRANSMISSION 9 Sheets-Sheet 1 FiledMarch 2'2, 193% 1953 9 sheets-sheet 2 R. E. MlLL-lCAN POWER TRANSMISSIONFiled March 27.

Nov. 8, 1938.

1933; R. E. MILLICAN- POWER TRANSMISSiON 9 Sheets-Sheet '5 Filed March237, 1953 I 3mm 20y f. MW/cam 1938- R E. MILLICAN 2,135,908

POWER TRANSMISSION Filed March 2'7, 1933 9 Sheets-Sheet 4 Roy .5.MY/(bcY/k I \j r JZZJ I Nov. 8, 1938. R. E-.'M|LLICAN ,135,

POWER- TRANSMISSION 9 Sheets-Sheet 5 Filed March 27, 1933 Nov. 8, 1938.R. E. MILLICAN POWER TRANSMI S S ION FiledMarch 2 7 19;; 1 9Sheets-Sheet e R. E. MILLICAN POWER TRANSMISSION FiledMaroh 2-7, 1953 9Sheets-Sheet 7 1938- I R. E. MILLICANI 2,135,908

POWER TRANSMI SS ION Filed March 27, 1953 9 Sheets-Sheet 8 Nov. 8, 1938.R. MILLICAN POWER TRANMISSION Filed March 2.7, 1933 9 Sheets-Sheet 9,Qoy f. Mf/ll'carx Patented Nov. 8, 1 938 I Q NITED STATES PATENT OFFICEPOWER TRANSMISSION Roy E. Millican, Dallas, Tex., assignor to L. R.Munger, trustee, Dallas County, Tex.-

Application March 27, 1933, Serial No. 662,971

52 Claims. (Cl. 74-293) This invention relates to new and usefulimwhenthe transmission is installed in a motor veprovements inpowertransmissions. hicle and it is desired not to use free wheeling.

The invention has to do with the method of An important object of theinvention is to protransmission of power, as well as the means for videa transmission including a high speed hytransmitting, and involves theautomatic gradadraulic clutch and a low speed hydraulic brake tion ofthe transmission of the power to the load, connected with a planetarygearing or other suitwhereby proportionate ratios .are set up and theable transmitting element, and these instrumendriving force is uniformlyapplied under varying talities so associated with a power shaft and aloads and speeds, and also whereby variations indrive shaftas totransmit power from the power v the R. P. M. of the power and drivingshafts are shaft to the drive shaft, at all speeds and loads, 10

co-ordinated. The method further involves the in direct ratio to therelative speeds and loads; automatic control of a high speed hydraulicclutch together with high and low speed governors or by the R. P. M. ofthe drive or load shaft'and controls actuated by the drive shaft andthethe control of a low speed hydraulic brake by the power shaft forautomatically controlling the hy- R. P. M. of the power shaft, togetherwith a'transdraulic fluid and the operation of the clutch 15 mittinggearing or other transmitting element inand brake.

terposed between and connected with the clutch A construction designedtocarry out the inv'en andbrake; whereby the power is applied from thetion will be hereinafter described, together with power shaft to thedrive shaft in exact proporother features of the invention.

tion or ratio, under varying loads and speeds; The invention will bemore readily understood and also whereby the clutch and brake autofrom areading of the following specification and matically become over-runningwhen the R. P. M. by reference to the accompanying drawings, in

of'the drive shaft exceeds that of the power shaft. which an example ofthe invention is shown, and

One object of the invention is to provide an wherein:

5 improved power transmission of the hydraulic Figure 1 is alongitudinal vertical sectional view 2 type, which will be moreeflicient, as well as more of a transmission constructed in accordancewith flexible and capable of performing a greater amthe invention andshowing the parts in normal plitude of functions, than those which havebeen or starting position,

heretofore produced. I Figure 2 is a similar View showing the trans- Aparticular object of the invention is to commission shifted to a highspeed position, 30 bine in a single transmission assembly the func-Figure 3 is an enlarged transverse sectional view tions of a clutch, avariable speed transmission taken on the line 33 of Figure 1, and anover-running clutch. Figure 4 is an enlarged transverse vertical sec- Afurther object of the invention is to provide tional view taken on theline 4-4 of Figure 1,

in such an assembly means controlled by the Figure5is an enlargedtransverse sectional view 35 speed of the engine or power unit forautomattaken on the line 5-5 of Figure 1, ically actuating the elements,whereby clutch and Figure 6 is an enlarged transverse sectionaltransmission operating pedals, levers, and the view taken on the line6-6 of Figure 1, like, may be dispensed with. Figure '7 is an enlargedtransverse sectional Another object of the invention is to provide anview taken on the line 'l'l of Figure 1, 0 p v variable speedtransmission, wherein Figure 8 is an enlarged transverse sectional fixedor graduated gear ratios are eliminated View taken on the line 3 ofFigure 2 and power transmission is accomplished i 11 Figure9 is anenlarged transverse sectional view rect ratio to the load imposed andthe power taken on the line of Figure 2,

4a til l ai r ifiher object of the invention is to pro Figure 10 is aView of the rear portion of the vide manually operated means, wherebythe astralismlsslon' elevamon and partly-m sembly may be locked in aneutral position, thus i k permitting the engine to be run at various spd Figure 11 is a transverse sectional view a en v on the line I I-l l ofFigure 10,

50 for desirable urposes without transmittin ower t t drive 2 m g pFigure 12 is a ..ectional view taken on the line A still further objectof the invention is to |2|2 of Figure provide manually operated meansfor adjusting Figure 13 is a partial longitudinal vertical secthe partsso that the over-running clutch functional view taken on the line l3-I3of F1gtion will be eliminated, which is highly desirable ure 3, 55

Figure His 8. vertical sectional view showing thepump drive, and

-Figure 15 is a cross-sectional view taken on line l5-l5 of Figure 12.

General assembly In the drawings the numeral III designates a housing orcase, which is divided into a forward or front section A and a rearsection B. The

section A may have its forward portion shaped in engine shaft l2 and adrive or transmission shaft I3. These shafts are disposed longitudinallyof the housing and are tubular. As is best shown in Figures 1 and 2, thepower shaft has its rear end l2 reduced and telescoping the forward endof the drive shaft |3,,but is rotatable independently thereof. A flangeI4, or other suitable element, may be provided on the forward end of thepower shaft for attaching to the crank shaft, or other driving elementof the engine or motor to which the transmission is connected.

The transmission includes primarily a high gear clutch assembly, which Ihave designated by the letter H, and a low gear brake assembly L,connected by a planetary gear assembly P interposed therebetween, all ofwhich is shown in Figures 1 and 2. While I have shown and 'described aplanetary gearing, it is to be understood that any gearing ortransmitting element suitable for the purpose may be used. The low gearbrake assembly L is interposed between the case sections A and B,while'the assembly H is mounted nearer the front end of the section A,and the assembly P near the rear end of the section A. Other importantelements of the transmission are a low gear governor F and a high geargovernor R. The governor F is mounted' at the front of the transmissionon the.rear side of the flange l4, while the governor R is mounted onthe drive shaft l3 within the section B. It will be understood thatthegovernor F is controlled by the speed of rotation or R. P. M.

of the power shaft l2, while the governor R is controlled by the speedof rotation or R. P. M. of

the drive shaft I3.- I v "The high gear clutch assembly The assembly Hincludes circular housing I plates I5 and" receiving therebetween aneccentric ring I! fastened in place by bolts i8, asis best shown inFigures 1, 2, 4 and 8. The ring I! has a concentric outer peripheryconcentric to the shaft l2, and an eccentric inner periphery or bore.The power shaft l2 extends axially through the plates l5 and I6 and hasan integral concentric head-l9 provided with collars 20 secured theretoby bolts 2I.' The collars extend beyond the periphery of the head andflt within recesses 22 in the housing plates II and It.

'An eccentric floating'bushingfl is rotatably mounted in the spacebetween the head and the ring IT. This bushing is confined between thecollars 20 and the housing plates and has a. concentric outer peripheryin constant contact with the eccentric bore of the ring, and aneccentric inner periphery or. bore of greater diameter than the head, soas to provide a space or chamber l9.

between the head and bushing. The bushing has a limited rotation in thebore of the ring and the head may rotate in the bushing, as well asindependently of the housing plates II and I0. The head is provided witha plurality of transverse slots which co-act with the collars 2| to formpockets 24, as is best shown in Figures 4 and 8; and transverse blades25 are mounted in these pockets. The outer ends of the blades arerounded so as to contact and form fluid-tight joints with the eccentricbore of the bushing 23.

The housing plate I5 is provided with a hub 26 having longitudinalexternal guides 21 receiv- .ing the splines 28 (Figures 1 and 2) of aslidable locking collar 29. The power shaft I 2 includes a'removablesleeve I 4', which is splined on said shaft and is formed integral withthe flange i4. This sleeve is merely a convenience in manufacture tofacilitate the placing of the parts of the assembly H on the shaft I 2,.and any suitable structure could be used.

The sleeve l4 carries a flange 30 having teeth By sliding the collar 29forwardly and engaging its splines 28 between the teeth ii, the housingof the assembly H is locked to the power shaft and caused to revolvetherewith. This eliminates any over-running clutch feature, such as isused in free-wheeling".- When it is desired to utilize the over-runningclutch feature, the collar 29 is slid rearwardiy, as is shown in Figures1 and 2. For operating the collar 20, I have shown a yoke 32 pivoted inthe section A i and attached to a cable 33, which extends to a suitableoperating means (not shown).

The rear housing plate i6 is provided with a 'hub 34 and the power shaftI 2 is suitably journaled in the hubs 26 and 34 of the assembly H.

' The hub 34 hasfastened thereon a flanged bear- The low speed brakeassembly This ring is mounted The low speed brake assembly is somewhatsimilar to the high speed clutch assembly, and is best shown in Figures1, 2, 5, 9, 10, 12 and 13. The assembly housing is formed by an inwardlydirected annular flange 40, which may be made a part of the front end ofthe section B of the case ill. The front side of the housing is formedby a circular stepped plate 4| mounted against an internal circularflange 42 in the rear end of the section A. An eccentric ring 43 isfastened between the flange and the plate 4| by means of bolts 44, whichare screwed into the flange 42. The parts just described also form arigid connection between the sections A and B of the housing. The ring43 has an eccentric bore like the ring I! and is immovable.

An elongated sleeve 45 is suitably Journaled on the shaft I3. Thissleeve has an' annular head 46 preferably integral therewith andprovided with a concentric outer periphery, similar to the head I9.Collars 41 surround the sleeve on each side of the head and are fastenedto the latter by bolts 48. The sleeve 45 is rotatably mounted intheplate 4| by means of a roller bearing (Figures 1 and 2) of suitableconstruction.

By this arrangement the sleeve 45, the head 46,

the housing formed by the elements 40 and 4|, the latter being heldstationary at all times.

The collars 41 extend beyond the head and are flush with the flange 40and the opposite side of the plate 4|. In this housing is mounted afloating eccentric bushing 50. The bushing 50, like the bushing 23, hasa concentric outer periphery and an eccentric bore and may, therefore,rotate in the ring 43; with which it constantly contacts. The bore ofthe bushing is greater in diameter than the head,'whereby a chamber 50is provided therebetween. The head 46 is provided with transverse slotswhich co-act with the collars 41 to form radial pockets receivingradially sliding gates 52 having their outer edges rounded so as tocontact and form fluid-tight joints with the bore of the bushing 56.

The planetary gear assembly It will be noted that there is no directconnection between the sleeve 45 of the low gear brake assembly L andthe drive shaft I3; nor

is there any direct-connection between the power shaft l2 and the driveshaft l3. This requires connection to be made from the assembly Lthrough the planetary assembly P to the shaft l3 and from the powershaft I2 and the assembly H through the assembly P to the said shaft I3.

A flanged ring 60 is secured on the reduced end of the hub 34 of theassembly H, as is best shown in Figures 1 and 2. This ring is secured onthe hub by means of keys 6| and is held in place by a retaining ring 62screwed onto the end of said hub. When the housing of the assembly H isrevolved the ring 69 will be revolved therewith. A spider 63 is securedto the ring 69 by bolts 64 and this spider carries stub shafts 65. Onthe forward end of the shaft I3 I provide an integral spider 66 formedwith forwardly extending bosses 6'I abutting the spider 63, whereby thespiders are spaced apart. Bolts 68 passing through the spiders andbosses are used to fasten the same together. It will be apparent thatthere is a positive driving connection between the housing plate l6 andthe drive shaft |3 by-means of the rigid connections between the spiders63 and 66. Thus motion may be transmitted direct without variation fromsaid housing to said shaft.

The sleeve 45 of the low gear assembly L extends forwardly beyond thebearing 49 and is reduced to receive the collar 69 of a planetary bellhousing Ill. The housing is fastened on the sleeve by a key'll and aretaining ring 12, similar to the ring 62. Motion is transmitted to thesleeve and its head 46 by the planetary housing. An internal gear ring13, shown in Figures 1, 2 and 7, is suitably fastened in the mouth ofthe housing 18 and is movable therewith. Pinions I4,

Journaled on roller bearings 15 on the shafts 65,

mesh with said gear. These pinions surround and mesh with a sun-pinion16, which is fastened on the reduced end l2 of the power shaft l2.

From the foregoing it will be apparent that power may be transmitteddirect from the shaft l2 to cause the sun-pinion to rotate the pinions14. When" the high gear clutch assembly H is locked, as in Figure 8, thespider 63 revolves with,

the shaft l2 and carries the pinions 14 with it. However, said clutchhousing may revolve independently of the shaft l2, thus causing thepinions 14 to travel around the sun-pinion 16. If the planetary housingis free to revolve then the pinions 14 may revolve, although theirshafts 65 are stationary, but whenever the high gear clutch assembly His locked with relation to the Figure '1.

shaft l2 then the pinions 14 and I6 become locked so that the planetaryhousing I0 is rotated.

It is obvious that whenever the head 46 of the assembly L is free torotate, then the'sleeve 45 and the planetary housing I0 with its ring"are free to rotate. Whenever the rotation of the head 46 isrestrainedthen the rotation of the sleeve 45 and the housing III are likewiserestrained.

The speed governors The tubular shafts l2 and |3 have coincidental boresfor receiving a tubular valve 80. A valve rod 8| is mounted to slideaxially in the valve. The valve 80, as is shown in Figures 1, 2, 4 and8, includes a head 82, a barrel 83, and a cylindrical plunger 84. Thefunction of this valve is to control the flow of the hydraulic fluid,

A collar 85 is fastened on the rod 8| near the low speed governor F atthe forward end of the shaft H. A coiled spring 86 is confined on thisrod between the collar and the head 82. When the spring expands it actsto move the valve and rod in opposite directions. In Figure 2 the springis shown as compressed and in Figure 1 it is shown as expanded.

The low speed governor For operating or reciprocating the rod 8|, thelatter is provided with annular teeth 81 at its forward end meshing withtoothed segments 88 forming part'of the governor F. These segments arepivoted on pins 89 carried by the flange l4 and the segments swingthrough slots 98 in the shaft l2 and its sleeve M. The segments carry-weights 88' which act to swing said segments outwardly, due tocentrifugal action, when the shaft l2 and the flange H are rotated. Whenthe segments are swung the rod 8| will be reciprocated. In Figure 1 thesegments rest against the rear side of the flange 4 and are in theirnormal or inner position. In Figure 2 the segments have been swungoutwardly to their limit and into contact with the flange 4. When thesegments swung from the position shown in Figure 1 to the position shownin Figure 2, the

- rod 8| was moved rearwardly and the spring 86 was partiallycompressed. v

The high speed governor The rear governor R includes segments 9| pivotedon pins 92 carried by the drive shaft l3 and engaging circular teeth 93through slots 94 in said shaft. The teeth 93 are formed on the rear.portion of the valve 89. The segments 9 have weights 9| and stop fingers95. When the power unit is rotating the shaft I! at idling speed theparts will be in the position shown in When a high speed is attained,the weights 9| rotating with the shaft 3 will swing outwardly to theposition shown in Figure 2, whereby the fingers 95 will engage the shaftI3 and limit further swinging of said segments. When the segments 9| areswung outwardly the valve 80 will be moved forwardly to the positionshown in Figure 2, against the tension of the spring 86, which will thenbe fully compressed.

The hydraulic system A centrifugal pump 96 is secured to the bottom ofthe section A of the case l0 on one side of the sump II. This pump isdriven from a worm gear 91 on the sleeve M, as is shown in Figure 14.'The drive shaft 98 of the pump extends up through a pedestal 99 mountedin the case and has a worm I on its upper end meshing with the gear 31.The pump is driven at about one-half the rate of speed of the powershaft I2.

011 from the sump is taken into the pump through a pipe IN anddischarged from said pump through a pipe I02. The pipe I02 hasconnection with a T I03 which is screwed into the bottom of the case I0.so as to connect with a vertical passage I04-extending upwardly in thepedestal 31. The passage I04 (Figures 1, 2 and 6) connects with anannular duct I05 in the hub 34 of the high speed'clutch assembly H, asis best shown in Figure 6.

The duct I05 connects with an internal duct I08 in the bore of the hub34 by means of ports I01. A port I00 extends through the shaft I2 fromthe duct I05 to supply oil to those portions of the shafts I2 and I3confined between the barrel 33 and the plunger 84. One of the ports I01in the hub 34 connects with a by-pass I09 (Figure. 2) which extendsthrough the housing plate I 3 into the ring I1, as is shown in Figures2, 4 and 8. A port IIO leads from the by-pass through the ring I1 to anarcuate duct III formedcentrally in the outer periphery of the bushing23. Ports II2 lead from the ends of the duct to the bore of the bushingand the chamber I8 and an intermediate port II3 leads from said duct. tosaid bore and chamber.

chamber I8 within the bushing 23 may ,receive its oil from the ports H2and H3 or it may receive it from the valve 80. The barrel 33 is providedwith longitudinal ducts 83', where'- by the oil flows through saidbarrel to the head 32. As is shown in Figures 1, 2 and 4, the shaft I2has .an annular duct H4 in its bore located between the head 82 and thebarrel 83 for receiving oil. Passages II5 substantially. tangent to theduct II4 extend from the latter to the periphery of the head I3 anddischarge into the chamber II. The circulation .of oil may be to andfrom the chamber by way of either the passages H5 or the ports H2 andH3. It will be observed that for each gate 25 one of the passages Iii-is provided and on the op osite side of each gate a port II5 extendsfrom the bottom of the pocket 24 to the periphery of the head. When theparts are in the position shownin Figures 1 and 4, the oil may freelycirculate through the head, bushing and ring, and the gates 25 are freetomove inwardlyand outwardly so that the high speed clutch is inactive.

For supplying oil to the low gear brake assembly L, a port II1 extendsthrough the shaft I3 to an annular duct II8 (Figures 1, 2, 5 and 9) inthe bore of the sleeve 45. Passages II3 extend substantially at atangent from the duct to the outer periphery of the head 45 to supplyoil to the chamber 50'. One of the passages H9 is provided at one sideof each gate 52 and ports I20 extend from the bottoms of the pockets 5|on the opposite side of each gate.

For supplying oil to the bore of the ring 43, I provide pipes I2I andI22, shown in Figures 1 and 2, as connected to a Y-coupling I 23;which ais free to rotate and the gates 52 may slide vtion and includes anadjusting nut I29 and, a

spring I 30, whereby it may be set to undergo: a predetermined pressurebefore opening. when the valve. does o'pen, oil is discharged intothesection A of the case I0 and drains into the sump II. Whenever oilceases to flow through the system the valve I28 will be opened and theoil by-passed from the 1' I03 into the case, as is obvious.

The low speed brake values In order to prevent or restrict the flow ofoil through the passages H9, I mount in the head 46 and the collar 41cylindrical slide valves' I3l, as is best shown in Figures 1, 2, 5, 9and 13. These valves are larger in diameter than the passages H8 andhave ports I32 adapted to register with said passages when the valvesare slid inwardly;

as is shown in Figures 1, 5 and '13, but whereby said passages areclosed when the valves are slid outwardly, as is shown in Figures 2 and9. The valves have mutilated circular heads I33 (Figures 1, 2 and 3)grooved to receive an annular flange I34 carried by a collar I35slidable on the shaft I3 and rotatable therewith.

The valve rod 8i extends into the plunger 84 and carries diametricallyopposite pins I36 which extend through longitudinal slots I31 in theplunger and wider slots I38 in the shaft I3 to the collar I35 in whichthey are fastened. Antifriction rollers I33 are mounted on the pins inthe slots I38. It is obvious that whenever the valve rod Si isreciprocated the collar I35 is slid and the valves I3I are either openedor closed The bushing stops For limiting the rotation or circumferentialmovement of the bushing 23 in the ring I1, I

fasten in the periphery of said bushing a key I43,

which has a sliding fit in an arcuate recess I in the inner periphery ofthe ring, as is best shown in Figures 4 and 8. This key bisects the ductIII and the oil is retained on each sideof the key and cannot passaround the same. It is pointed out that when the key I40 is at the right(Figures 4 and 8) of the recess I, the eccentric bore of the bushing 23will be eccentric to the outer periphery of the head I9. If said key ismoved to the other end of said recess and the bushing rotated to theleft (Figures 4 and 8),

said bushing will be rotated around the head and its bore will becomesubstantially concentric to said head. In the first position the partsare in driving position, but in the second position the parts areadjusted to over-running relation.

A similar key I42 is fastened in the outer periphery of the bushing 50in the low gear brake assembly L, as is best shown in Figures 5 and 9.This key bisects the duct I28 and engages in an arcuate recess I43, andits operation is similar to that of the key I40. The lengths of therecesses HI and I43 determine the amplitude of rotation or oscillationof the bushings 23 and 50.

High gear locking assembly In order to lock the entire transmission inhigh gear or direct drive, whereby it is made non-automatic; or inneutral position, so as to render it inactive or non-responsive when theengine or motor is operating, 1 have provided the mechanism shown inFigures 10, 11 and 12. In the outer periphery of thebushing 50, Iprovide an arcuate duct I50 and a key II at the end of said duct. Thiskey, similar to the key I42 and shown in Figures 5 and 9, has a slidingfit in an arcuate recess I52 in the inner periphery of the ring 43'. Aport I53 connects a cylindrical passage I54 in the ring with said duct.Thispassage extends transversely through the flange 40 of the casesection B and through the housing plate M, as well as through the ring.The pipe I22 hereinbefore referred to as extending from the pumpassembly, is-tapped into the ring 43 and connects with'the passage I54through a port I55 at the central portion of said passage. Itwill benoted that the port I53 and the duct I50 are located forwardly or to oneside of the port I55, and thisv will be evident from an observation ofFigures 10 and 12.

A piston valve I56 is slidably mounted in the 50 will be shifted to theposition shown in Figure 9. In order to permit the key I5I to freelymove, a breather port I52 (Figures 9 and 10) is provided at the end ofthe recess I52 and this port extends through the plate 4| to the case.When,

the parts are in this position, the head 46 of the low gear brakeassembly will be free to rotate in the bushing.- When (the valve I56 isslid outwardly or rearwardly, its head will stand between the ports I53and I55 and, therefore, oil from the duct I50 may flow out into thepassage I54 and escape into the section A of the case I0.

This valve is manually operated and is attached to the end of an arm I58extending from a collar I59 which is fastened on a shaft I60, as isshown in Figure 10. The shaft is slidably mounted in a. packing glandI6I and also in the rear wall of the case. A wire I62 is suitablyattached to the shaft and extends to a convenient operator (not shown),which may be located on the dash board of a motor vehicle or at someother suitable point. By pushing this wire the shaft is slid rearwardlyand by pulling on said wire the shaft is moved forwardly.

When the valve I56 is closed to cause the transmission to shift into aneutral position, it is necessary to lock the high speed governor Ragainst operation. For this purpose a grooved collar I63 (Figines 1, 2and 11) is rotatably mounted on the shaft I3 in the.rear portion of thesection B of the case I0. The collar is provided with an overhangingannular flange I64 of such size as to engage between the stop fin gers95 of the segments 9|, when the same are in the position shown in Figure1, and said collar is slid forwardly. The low gear brake head 46 thusrotating the sun-pinion I6, which in turn will rotate the pinions I4(Figure '7) on their shafts 65.

For locking the high gear in direct drive and thereby eliminating theautomatic feature, the

collar may be slid forwardly when the parts are in the adjustment shownin Figure 2. The flange I64 will ride over the fingers 95, therebylooking the governor R; in its full operative position. For shifting thecollar I63, a yoke I65 is connected in the groove of said collar madeintegral with a sleeve I66 fastened on the shaft I60. It will beapparent that when the wire I62 is pulled forwardly, the valve I56 willbe slid to its open position and the collar I63 will be slid to lock thehigh speed governor in its extended position.

Operation Assuming the power shaft I2 to be revolving at the idlingspeed of the motor or engine by which it is driven, the parts will be inthe position shown in Figures 1, 4 and 8, and the transmission of motionor power. will flow in the direction indicated by the arrows. The highspeed clutch assembly H will be in the position shown in Figure 4 andthe head I9 will be turning in a clockwise direction, which is thedirection of rotation of the power shaft I2. The low gear brake assemblyL will be in the position shown in Figure 5 and the head 46 will beturning in a counter-clockwise direction, because the housing 10 of theplanetary assembly P will be revolved in a reverse direction to theshaft I2 through the agency of thepinions I4 (Figure 7), which arerotated by the sun-pinion I6 fastened on said shaft.

With the valve 80 positioned as shown in Figures 1 and 6, the oil mayfreely flow from the pump 96 by way of the conductors I02, I03 and I04to the annular duct I05. From theduct I05 the .oil flows through theports I 01 to the duct I06. The 'oil also flows from one of the portsI0I (Figure 6) through the by-pass -I09 (Figure 2) and port IIO to theduct III and thence by way of the ports H2 and H3 to the chamber I9between the bushing 23 and the head I9. The oil which flows into theduct I06 flows therefrom through the port I00 to the valve 80 in theshaft I2, as is shown in Figures 1 and 6. This oil passes through theducts'83' to the annular duct H4 in the head I9 (Figures 1 and 4). Fromthe annular duct II 4 said oil flows through the tangential passages II5, which are also open at their outer ends to the oil which wasdelivered to the chamber I9 between the head and the bushing.

It will be obvious that as the head rotates the gates 25 will be free tomove radially because the how of the oil is unrestricted and it mayfreely circulate through the passages I I5 and I I6, chamber I9 andports H2 and H3.

The oil which is delivered to the valve 80 andconfinedin the shafts I2and I3 by said valve will 'flow through the port I I'I (Figures 1 and 5)to the annular duct H8 in thesleeve 45. From the duct II8 the oil isfree to flow through'the tangential passages II9 because the pistonvalves I3I will be open (Figures 1 and 5) and their ports I32 willregister with said passages. The pump 96 will also supply oil to thepipe I2 I, which will deliver oil to the port I24 (Figures 1, 5, 9 and12),- from which it will flow to the arcuate duct I26 in the "outerperiphery of the bushing 50. From this duct said oil is conducted by theports I2I to the chamber 50 between the head 4'6 and the bushing, whichchamber is also open to the tangential passages II9, whereby the flow ofthe oil is unrestricted and the gates 52 are free to move radially.

From the foregoing, it will be obvious that when the transmission is inits idling or starting position, the clutch and brake .will be inactivei are closed and the gates locked into position, the

because the oil will be-free to flow through the entire system, thesurplus being discharged by unseating the relief valve I28, as is shownin Figure 6. The term oil has been used in a generic j sense and anyliquid suitable for the purpose may be used. It' is pointed out that theclutch and brake may be rendered inactive either by adjusting the valvesso as to'permit a free circulation .of the oil, whereby the gates and 52are free to move inwardly or. outwardly, or by moving the chambertherebetween. Normally the bushing and head will be in eccentricrelation when the parts are idling and, therefore, when the valvesclutching o'r braking action will be almost instantaneous, and it willnot be necessary to shift either bushing in order to establish clutchingor braking relation.

When the speed of the motor or engine is increased to transmit power tothe load, the low When the circulation of oil through the pas; sages II9 is restricted by the partial closing of the valves I3I, or entirelyout off by the closing of said valves, the radial movement of the gates52 is either retarded or they are locked in their extended positionswith their outer ends in intimate contact with the inner eccentric 'boreof the bushing 58; The chamber 59' will trap the oil between the gates,and owing'to'the eccentric shape of the bore of the bushing the circularhead will be prevented fromrotating. The trapped oil will lock theassembly L, whereby the planetary housing I0 will be held againstrotation because of its rigid attachment to the sleeve 45 on which the'head .46 is fastened. This action will cause the pinions I4 to travelaround the ring gear I3 in a clockwise direction (Figure 7), thusimparting rotation to. the spider 66 and the drive shaft I 3. When thisoccurs an operation similar tothe shifting into low gear of an ordinarymotor vehicle transmission will have been performed.

As the speed or R P. M. of the power shaft I2 and the drive shaft I8increase, the high speed governors R will move outwardly, whereby thevalve 8II will he slid forwardly against the tension of the spring 88.When the barrel 83 is moved forwardly by the-operation of the high speedgovernor R to restrict or to cut oil the flow of oil from the ducts 83'to the duct I, as is shown in Figures 2 and 8, circulation of oilthrough the pasasges II5 of the head I9 is interrupted. If the duct I isonly partially closed, then a restricted flow will be provided and flowthrough the passages II5 will be in accordance. Upon the interruption-ofthe circulation of oil through the passages II5, by the shifting of thevalve 80, only the position of said valve will be changed, and theremaining clutch elements I will substantially retain their positions asis shown in Figures 4 and 8. Oil will be trapped in the chamber I9 andthe gates 25 will be locked or retarded, whereby motion will betransmitted l ill from the head I9 by means of the trappedo and bushing23 to the nu Il ofthehigh 'g'ear' clutch assembly H. The pow r shaft I2rotates the head I9 and rotationis contributed to the bushing and ringII. It is here pointed out that the movement of the valve and the valverod are absolutely at all times and at all speeds, above that ofstarting, under the automatic control of the governors F and R. Thevalve and'the' valve rod controlling the flow or circulation of the oilmay partially interrupt such flow or entirely out it off,

sion of power. 7 This is due to the hydraulic action. 7

The transmission of motion is'controlled by the gates 25, and if thesegates yield inwardly and permit the passage of oil at their outer endsthe head will rotate relatively of the bushing. By restricting the ofoil, the gates will yield sufficiently-to givga slippage or relativerotation of the-head in the bushing, but at the same time will rotatesaid b'iiishing at a reduced R. P. M. and the bushing will-Tin turnrotate the ring ll of the assembly H. If the flow of the oil is entirelyout off, as in Figures 2 and -8, then there will be no slippage and theassembly H will rotate at the same rate ofspeed .as the power shaft I2.

Owing to the hydraulic system'and action, the gates 25 may yield tovarious degrees up to actual locking. This is controlled by theactuation of the valve 88 by the variations in the centrifugal action.of the governor R, due to speed fluctuations. By such an arrangementsubstantially all gear ratios from low to high are set up between thehead and the bushing.

When the flow of oil is interrupted or cut off by the shifting of thebarrel 83 and the assembly H operated, as before stated, the spider 63,which is carried by the hub 34 of the high speed clutch, will rctate'atthe same rate of speed as'the power shaft I2, or at a lower rate,according to the flow of the oil. Rotation being transmitted to thespider 66 by the stub shaft 65, the transmission of power or motion willbe as is shown by the arrows in Figure 2. When this high speed drive isset up, the direction of rotation of the planetary housing I0 and thesleeve 45 and the head 46 will be reversed to that of idling operation,and the low gear brake thus becomes released, althoughits valves I3I arestill closed. This is caused by the gates 52 forcing oil through thecenter and right hand ports I21 and displacing the'key I42, whereby thebushing 58 is shifted to a nearly concentric position, as is shown inFigure 9. "The central port and the end port I21- co-act with the ductI26 in by-passing oil around a gate 52 lying therebetween. The head 48is now revolving in a clockwise direction the same as the power shaftI2,' and the gates move inwardly as they approach the ports I21, becauseof the oil by-passing as described. This explains the reason for thecentral port. The two ports also permit the passing of suflicient oil toshift the key I 42, as has been described.

Whenever the R. P. M. of the drive shaft I3 exceeds the R. P. M. of thepower shaft I ,2,the

assembly H becomes an over-running clutch be- I cause. the flow ofmotionwill be reversed from the shaft I3 through the planetary assemblyP to the hub 34, which will cause the ring II to A housing ring IT. Theright hand port I I2 (Figures 4 and 8) and the center port I I3 willco-act in this shifting. When the bushing is thus shifted, its bore willbe substantially concentric to the longitudinal axis of the shaft I2 andthe head I9 and, therefore, said bushing and the entire housing to whichthe ring I! is attached may rotate free of the head I9, which is beingdriven by said shaft. When the R. P. M. of the shaft I2 catches up withthat ofthe drive shaft I3 and advances, the head will then move into itseccentric position and again establish the clutching relation, as isshown in Figures 2 and 8. If it is desired to cut out the over-runningclutch feature, the locking collar 29 (Figures 1 and 2) may be slidforwardly by operating the cable 33,

whereby the housing of the assembly H is locked to the sleeve I I of theshaft I2 and caused'to turn therewith at all speeds.

When it is desired to adjust the transmission to a neutral position,whereby the motor may be stopped, started, or run at any speed withoutimparting motion to the drive shaft I3, the cable I62, as shown inFigure 10, is pulled to slide the shaft I60 forwardly, whereby the yokewill slide the collar I63 forwardly. The flange I64 will ride betweenthe fingers 95, because thesame will be in the position shown inFigure 1. This will lock the valve in the position shown in Figure 1,whereby the shaft I2 and the head I9 may rotate independently of thehousing of the high gear assembly H.

When the shaft I66 is slid forwardly for the above adjustment, the valveI56 will be shifted to the position shown in Figure 10 and communicationwill be established between the ports I53 and I55 (Figures 10 and 12).Oil flowing from the pipe I22 will be supplied through the port I53 tothe duct I50 (Figure 9) from which it will flow into the recess I52. Thepressure of the oil against the key I5I will shift the bushing 50 into aposition, whereby its inner bore will be substantially concentric to thehead 46, which will render the low gear assembly inactive.

When it is desired to throw the transmission out of its neutralposition, the cable I62 is pushed to slide the shaft I60 rearwardly.This withdraws the collar I63 and releases the high speed governor R. Atthe same time the valve I56 is withdrawn to interrupt the flow of oilbetween the poi'ts I53 and I55. The oil in the duct I50 and recess I52will then be free to flow through the port I53 into the passage I54beyond thehead of the valve and exhaust into the section A of the caseI0. It is obvious that with the high speed governor R in its fulloperative position, as shown in Figure 2, the collar I63 may be slidforwardly so thatthe flange I64 will engage over the fingers and lockthe parts iii-high gear.

The description which has been given recites more or less detail of aparticular embodiment of the invention, which is set forth as new andureful, however, I desire .it understood that the invention is notlimited to such exact details of construction because it ismanifest thatchanges and modifications may be made, within the scope of the appendedclaims, without departing from connected with the power shaft and withsaid transmitting element, a low speed governor operated by the powershaft, controlling means for the low speed brake operated by the lowspeed governor, a high speed governor operated by the drive shaft,controlling means for. the high speed clutchoperated by the high speedgovernor, and means for locking the high speed, clutch to the powershaft to render said clutch inactive.

. 2. A transmission comprising, a power shaft, a drive shaft, a gearingconnected with the shafts, a

hydraulic low speed brake connected with the gearing, a'hydraulic highspeed clutch connected with the power shaft andwith the gearing, "a

valve forcontrolling the hydraulic action of the low speed brake, avalve for controlling the hydrauilcaction of the high speed clutch,means connected with and actuatedby the power shaft having connectionwithth valve of the. low

speed brake for actuating the same, and means connected with andoperated by the drive shaft having connection with the valve of the highspeed clutch for actuating the same,

3. A transmission comprising, a power shaft, 9. drive shaft, a gearingconnected with the shafts, a hydraulic low speed brake connected withthe gearing, a hydraulic high speed clutch connected with the powershaft and with the gearing, a valve for controlling the flow of fluid inthe low speed brake, a valve for controlling the flow of fluid in thehigh speed clutch, a low speed governor connected with and operated bythe power til shaft having connection with the low speed brake fluid. inthe high speed clutch, a low speed governor connected with and operatedby the power shaft having connection with the low speed brake valve foroperating the same, a high speed governor connected with and operated-bythe drive shaft having, connection with thevalve of the high speedclutch for operating the same, and means for locking the high speedgovernor in one position whereby the high speed clutch is engaged and inanother position whereby said clutch is disengaged.

5. A transmission comprising, a power shaft, a'driv'e shaft; a gearingconnected with the shafts, a hydraulic low speed brake'connected withthe gearing, a hydraulic high speed clutch connected 'with the powershaft and with the gearing, a valve for controlling the flow of fluid inthe low speed brake for actuating the latter, means connected with thelow speed brake valve operated. by the power shaft and automaticallyvariable with the R. P. M. of the power shaft for coordinately operatingthe low speed brake and its valve, a valve for controlling the flow offluid inthe high speed clutch for actuating the lat ter, and meansconnected with the high speed I clutch valve operated by. the driveshaft and automatically variable with the R. P.- M. of the drive shaftfor coordinately-operating the high speed clutch and its valve.

6. A transmission comprising, a power shaft, a drive shaft, a gearingconnected with said Gil -with the gearing for controlling the operationof the drive shaft at low speeds, a high speed hydraulic clutchconnected with the power shaft and with-the gearing for controlling thedriving of the drive shaft at intermediate and high speeds, a liquidcirculating system connected with and extending through the clutch andbrake andincluding means for interrupting the circulation of liquidthrough said clutch and brake, and means automatically operated andvariable with the R. P. M. of each shaft for actuating the interruptingmeans of said system for controlling said clutch and brake coordinatelywith. the

variations in the R. P. M. of said shafts.

' 7. In a transmission, the combination with a driven member, a highspeed hydraulic clutch for driving said member having actuating meansautomatically operated by the driven member and coordinately withvariations in the R. P. M. thereof, and a low speed hydraulic brakehaving actuating means automatically operated'by the driving member andcoordinately with variations inthe R. P. M. thereof, of a gearingincluding a support connected to the high-speed clutch and the drivenmember, and transmitting gears connected with the support, .the lowspeed brake and the driving means.

8-. A transmission comprising, a power shaft, a drive shaft, atransmitting element connected with said shafts, a brake housingheldagainst rotation, a brake head connected with the trans mitting element,means hydraulically operated for connecting and disconnecting the headand housing, and means directly actuated by the power shaft forautomatically controlling the hydraulic operation.

9. A transmission comprising, a power shaft,

. a hydraulic high speed clutch, a transmitting of the-shafts, wherebythe power shaft drives the drive shaft in a direct ratio governed by theR. P. M. of the drive shaft.

10. A transmission comprising, a power shaft, ahead fastened to saidpower shaft, a clutch housing rotatable around said head, a transmittingelement connected to said housing, a drive shaft connected to saidelement, hydraulic means having provision for circulating a fluid in thehousing for clutching and unclutching with said 'head, means forinterrupting the circulation of the hydraulic fluid forcontrolling theoperation of the clutching means, and means actuated by the drive shaftand variable with the R.- P. M.

thereof for automatically operating said interrupting means forgoverning the clutching action, whereby the power shaft drives the driveshaft in a ratio variable with the R. P. M. of each shaft, the housingof the clutch being movable by the transmitting element to overrun thehead when the R. P; M. of the drive shaft exceeds the driving ratio.

11. As a sub-combination in a transmission, a

hydraulic clutch comprising, a driving member,

a housing surrounding the driving member and rotatable, the housinghaving a liquid circulating passage, a head withinthe housing rotatedwith and by the driving member and having a liquid passage extendingfrom its center to its outer periphery, hydraulic gates mounted in thehead, a rotatable eccentric bushing in the housing surrounding the head,a key on the bushing engaging the head for limiting the rotation of saidbushing in the housing and for rotating said bushing, the key being inthepath of the liquid in the circulating passage of the housing,

engaging the housing for limiting the rotation of saidsaid bushing inthe housing and for rotating bushing, a head rotatable within thebushing and having a liquid passage therethrough, hy-

draulic gates mounted in the head and engaging within the bushing, meansfor supplying liquid to the liquid passages, means for controlling thecirculation of the liquid through the passage of the head forcontrolling the gates, a driven element connected with the head, andmeans sotuated by the driving member for automatically operating thecontrolling means.

13. A transmission comprising, a power shaft, a drive shaft, atransmission connected with said shafts, a hydraulic high speed clutchconnected with the gearing and the power shaft and normally unclutched,a hydraulc low speed brake connected with the gearing and normallyreleased, means for locking the high speed clutch in'its unclutchedrelation, means for controlling the hydraulic action of the low speedbrake to shift it to its released relation, and means for jointlyactuating the high speed clutch lock and the hydraulic control, wherebythe transmission is locked in neutral position.

14. As a sub-combination in a transmission, a hydraulic clutchcomprising, a housing held against rotation, an eccentric bushingrotatable in the housing, a head rotatable in the bushing and co-actingtherewith to establish clutching relation therebetween, a projectioncarried by the bushing and engaging the housing for controlling therotation of the bushing relatively of the head and housing, the housinghaving a liquid passage extending to said projection for supplyingpressure fluid thereto to move said projection, a. .valve controllingthe flow of fluid through the passage of, the housing, means foroperating said valve to control the rotation of said bushing by theliquid.

15. A transmission including, a power shaft, a drive shaft, a.transmission gearing connected with the shafts, a clutch housing havinga liquidpassage therethrough, a bushing rotatable in the housing andhaving a liquid passage therethrough, a head rotatable in the bushingand having liquid passages therethrough, hydraulic gates movable in thehead and ensu g the bushing, means exposed to the liquid passing throughthe housing and bushing for rotating said bushing within the housing,valves carried by the head movable to open and close the passagesthereof,

tatably connected, and an operating. element between the governor andsaid shifting element.

16. A transmission including, a power shaft, a drive shaft, atransmission gearing connected with said shafts, a clutch housing havinga liquid passage therethrough, a bushing within the housing having aliquid passage therethrough, a head fastened on the power shaftrotatable in said bushing and having liquid passages therethrough,hydraulic gates in said head engaging in said bushing, said bushingco-acting with gates to establish a fluid lock and with said housing totransmit motion, a valve for controlling the supply of liquid to saidhead, and a governor connected to the drive shaft and also connected tothe valve for operating the same.

17. Atransmission comprising, a power shaft, a drive shaft, atransmitting element connected with said shafts, a high speed clutchhousing attached to said element, a clutch head in said housing attachedto the power shaft, means bydraulically'operated disposed between thehead and the housing for clutching and unclutching said head andhousing, and a high'speed governor connected with and operated by thedrive shaft for controlling the hydraulic action, where-. by the headand housing are clutched and unclutched.

18. Atransmission comprising, a power shaft, a drive shaft, atransmitting element connected with said shafts, abrake'housing heldagainst rotation, a brake head connected with the transmitting element,means hydraulically operated for connecting and disconnecting theheadand housing, and a low speed governor directly connected with andoperated by the power shaft for controlling the hydraulic operation;

19. As a sub-combination in a transmission, a hydraulic clutchcomprising, a driving member, a housing surrounding the driving memberand rotatable, the housing having a liquid circulating passage, a headwithin the housing rotated with and by the driving member and having aliquid passage extending from its center to its outer periphery,hydraulic gates mounted in the head, a bushing surrounding the headwithin the housing and connected with said housing, said bushing havinga liquid passage therethrough, said bushing coacting with gates toestablish 'a fluid lock and with said housing totransmit motion, adriven element connected with the housing, and means automaticallyactuated by the driven element for controlling the circulation of liquidthrough the liquid passage of the head.

20. The combinationin a transmission, of a tubular powershaft, a tubulardrive shaft, a hydraulic, low speed brake surrounding the drive shaft, ahydraulichigh speed clutch surrounding the power shaft, a planetarygearing connected with the shafts and the clutch ,and' brake, a

valve slidable in the power shaft for controlling the circulation of thehydraulic fluid in the high speed clutch, valves movable in-the lowspeedbrake for controlling the circulation of the hydraulic fluid, a highspeedgovernor connected with the drive shaft and the slide valve foroperating said valve, a low speedgovernor connected with the powershaft, a valve shifter connected with the low speed brake valves, and arod slidable through the slide valve operated by the low speed governorand connected'with th sh ter for actuating said shifter and said lowspeed brake valves.

21. The combination in a transmission, of a I power shaft, a driveshaft, a clutch head fastened on the power shaft, a clutch housingrotatable around said head, hydraulic clutching means enclosed thereby,a spider rigidly connected with the clutch housing, a second spiderrigidly connected to the drive shaft, rigid connections between saidspiders, pinions mounted on said connections, a sun-pinion meshingwiththe pinions and mounted on the power shaft, a housing having a gearmeshing with the pinions, a stationary brake housing, a sleeve rotatableon the drive shaft andrigidly connected to the gear housing, a. headfast upon the sleeve and rotatable within the stationary housing, ahydraulic braking means in said stationary housing, the clutch and brakehou ings and heads having fluid circulating passages, means forcirculating fluid through the passages, means for controlling thecirculation of the fluid, and means operated by the shafts and governedby the variations in the R. P. M. thereof for automatically actuatingsaid fluid controlling means for controlling the hydraulic clutching andbrakingmeans in accordance with;

the R. P. M. variations of said shafts.

22. The combination in a transmission, of a power shaft, a drive shaft,a clutch head fastened on the power shaft, a clutch housing rotatablearound said head, hydraulic clutching-means enclosed thereby, a spiderrigidly connected with the clutch housing, a second spider rigidly comnected to the drive shaft, rigid connections between said spiders,pinions mounted on said connections, a sun-pinion meshing with thepinions and mounted'on the power shaft, a housing having a gear meshingwith the pinions, a stationary brake housing, a sleeve rotatable on thedrive shaft and rigidly connected to the gear housing, a head fast uponthe sleeve and rotatable within the stationary housing, hydraulicbraking means in said stationary housing, the clutch and brake housingsand heads having fluid circulating passages, means for circulating fluidthrough the passages, means for controlling the circulation of, thefluid, a'low speed governor carried by the power shaft, a high speedgovernor carried by the drive shaft, and connections between clutchincluding, a rotatable housing having a fluid passage therethrough, abushing oscillating in said housing and having a fluid passage, thehousing having a recess open to the fluid passage of the bushing, aprojection on the bushing extending into said housing recess, a headrotatable in the bushing and having fluid passages extending to itsouter periphery, radially movable gates in said head engaging thebushing, the head having fluid openings-extending from its outerperiphery to the inner ends of the gates, and a valve for controllingthe flow of fluid through the passages of the head.

24. As a sub-combination in a transmission, a clutch inc1uding,'arotatable housing having an eccentric bore and provided. with a fluidpassage extending therethrough, a circular bushing rotatable in thehousing and having an eccentric bore, said bushing having a fluidpassage, the housing having a recess open to the fluid passage of thebushing, a projection on'the bushing exchamber between said gates forcontributing rotation from said'head to said bushing and hous-' tendinginto said housing recess for imparting a limited rotation to thebushing, a circular head rotatable in the eccentric bore of the bushingand of less diameter, whereby a fluid chamber is formed between the headand the bushing, said head having radiating fluid passages open to saidchamber, radially movable gates in said head extending into said chamberand engaging the bore of the bushing, the head having fluid openingsextending from the inner ends of the gates to the chamber, and means forinterrupting the passage of fluid through the passages of the head,whereby said gates are held in engagement with said bushing and saidbushing is held in eccentric relation to said head for trapping fluid inthe ing, ,the bushing being rotatable into substantially concentricrelation to said head, whereby the housing and bushing may rotateindependently of the head.

25. As a sub-combination in a transmission, of a power shaft, a driveshaft, a rotatable housing having an eccentric bore'and provided with,

a fluid passage extending therethrough, a circular bushing rotatable inthe housing and having an eccentric bore, said bushing having a fluidpassage, the housing having a recess open to the fluid passage of thebushing, a projection on the bushing extending into said housing recessfor imparting a limited rotation to the bushing, a circular headfastened on the power shaft and rotatable in the eccentric. bore of thebush- N ing and of less diameter, whereby a fluid chamber is formedbetween the head and the bushing, said head having radiating fluidpassages open to said chamber, radially movable gates in said headextending into said chamber and en aging the bore of' the bushing, thehead having fluid openings extending from the inner ends of the gates tothe chamber, and means for interrupting the passage of fluid through thepassages of the head, whereby gates are held in a ement with saidbushing and said bush-.

ing is held in eccentric relation to said head for trapping fluid in thechamber between said gates for contributing rotation from said headto'said bushing and housing, the bushing being rotatable intosubstantially concentric relation to said head, whereby the housing andbushing may rotate independently of the head, a connection between thehousing and the drive shaft, and a governor operated by the drive shafthaving connection with the fluid interrupting means for operating thesame coordinately with the variations in the R. P. M; of the driveshaft.

26. As a sub-combination in a transmission, a

clutch "including, a rotatable housing having an eccentric bore andprovided with a fluid passage extending therethrough', a circularbushing ro tatable in the housing and having an eccentric bore, saidbushing having a fluid passage, .the housing having a recess open to thefluid passage of the bushing, a projection on the bushing ex-- tendinginto said housing recess for imparting a limited rotation tothe-bushing,- a circular head rotatable in the eccentric bore of thebushing andof less diameter, whereby a fluid chamber is formed betweenthe head and the bushing,.said head having radiating fluid passages opento said chamber, radially movable gates in said head extending into saidchamber. and engaging the bore of the bushing, the head having fluidopenings extending from the inner ends of the gates to the chamber,means for interrupting the passage reiation to said head, whereby thehousing and bushingmay rotate independently of the head, a

power shaft connected to the head, a drive shaft I connected to thehousing, and a shiftabie element for locking the housing againstrotation with respect to the power shaft.

. 27. As av sub-combination in a transmission, a clutch including, arotatable housing having an eccentric bore and provided with a fluidpassage extending therethrough, the housing having a recess in its bore,a circular bushing rotatable in the bore of the housing having aneccentric bore, said bushing having an arcuate duct in its periphery andprovided with ports extending from said duct to'its bore, a key inthe-bushing intermediate the ends of the duct engaging in the recess ofthe housing for shifting the bushing and for limiting its rotation, thefluid passage of the housing being open to receive fluid from anexterior source, a circular head rotatably mounted in the eccentric boreof the bushing and of less diameter, whereby a fluid chamber is formedbetween the head and the bushing, gates movable radially in said headextending into said chamber and engaging the bore of the bushing, thehead having fluid passages extending radially therethrough on one sideof the gates and fluid openings leading from the inner ends of saidgates to the periphery of the head on the opposite sides of said gates,the head at its center being open for an exterior supply of fluid to thepassages, and a valve for interrupting the supply of fluid to thepassages of the head for controlling theoperation of said gates.

28. As a sub-combination in a transmission, a brake including, astationary housing having an eccentric bore and provided with a fluidpassage extending therethrough,. a circular bushing rotatable in thebore of\the housing and having an eccentric bore, said bushing having afluid passage, the housing having a recess open to the fluid passage ofthe bushing, a projection on the bushing extending into said housingrecess for imparting a limited rotation to the bushing, a circular headrotatable in the eccentric bore of the bushing and of less diameter,whereby a fluid chamber is formed between the head and the bushingpassages open to tatable into substantially concentric relation to saidhead, whereby said head is released for rotation. v

29. As a sub-combination in a transmission, a brake including, astationary housing having an eccentric bore and provided with a fluidpassage extending therethrough, the housing having a recess in its bore,a circular bushing rotatable in the bore of the housing having aneccentric bore, said bushing having an arcuate duct in its pesaid ductto its bore, a key in the bushing intermediate the ends of the ductengaging in the recessof the housing for shifting. the bushing and forlimiting its rotation, the fluid passage of the housing being open toreceivefluid from an exte- 'rior source, a circular head rotatablymounted in the eccentric bore of the bushing and of less diameter,whereby a fluidchamber is formed between thehead and the bushing, gatesmovable radially in said head extending'into said chamber and engagingthebore of the bushing, the head having fluid passages extendingradiallytherethrough on one side of' the gates and fluid openingsleadingfrom the innerends of said gates to the periphery of the head on theopposite sides ofsaid gates, the head at its center being open for anexterior supply of fluid to the passages, valves slidable in the headthrough the radial fluid pas.- sages thereof the housing having anauxiliary fluid inlet, a valve controlling said inlet, a recess in thebore of the housing, connected with the fluid inlet and receiving fluidtherefrom, and a projection on the bushing engaging in the housingrecess last named.

30. The combination in a transmission, of a drive shaft, a power shaft.a high speed hydraulic clutch connected with the power shaft, agearingconnected with the shafts and the housing of the .high speed clutch, alow speed brake connected for controlling the low speed brake for movingit,

into neutral position, a high speed governor having-stop fingers andconnected with the valve of the high speed clutch for operating thesame, a slidable member for engaging the fingers of the governor forlooking it in its extended or retracted position, and means for shiftingsaid member connected with the low speed brake valve for operating thesame.

31. In a transmission, a tubular power shaft, a tubular drive shaft, agearing connecting said shafts, a hydraulic high speed clutch connectedwith the power shaft and the gearing, a hydraulic low speed brakeconnected with the gearing," a liquid circulating system connected withthe power shaft and the clutch and brake, a slide valve mounted in thepower shaft for controlling the fiow'of liquid to the high speed clutch,slide valves mounted in the low speed brake forcontrolling thecirculation of liquid therethrough, the'power shaft having openingstherein, the drive shaft having openings therein,high' speed governorsegments mounted on the drive shaft and extending through the openingsthereof, a plunger on the slide valve of the power shaft extending intothe drive shaft and engaging the segments thereof, a valve rod slidablymounted in the valve in, the shafts and having connection throughopenings in the drive shaft with the valves of the low speed brake, acoiled spring surrounding the rod and confined thereon to engage one endof the slide valve, and low speed governor segments mounted on the powershaft and having operative connection with the rod through the openingsof said shaft.

32. A transmission comprising, a power shaft, a drive shaft, atransmitting element connected with the shafts, a hydraulic low speedbrake connected with said element, a hydraulic high speed clutchconnected with the power shaft and with said element, a low speedgovernor connected with and operated by the power shaft, controllingmeans for the low speed brake connected with and operated by the lowspeed governor, a high speed governor connected with and operated by thedrive shaft, and controlling means for the high speed clutch connectedwith and'operated by the high speed governor.

33. A transmission comprising, a power shaft, a drive shaft, atransmitting element connected with the shafts, a hydraulic low speedbrake connected with said element, a hydraulic high speed clutchconnected with the power shaft and with said element,-a1ow speedgovernor connected with and operated by the power shaft, controllingmeans for the low speed brake connected with and operated by the lowspeed governor, a high speed governor connected with and operated by thedrive shaft, controlling means for the high speed clutch connected withandoperated by the high speed governor, and means for locking the clutchand brake in neutral position.

34. A transmission comprising a power shaft,

a drive shaft, a transmitting element connected means for the low speedbrake connected with and operated by the low speed governor, a highspeedgovernor connected with and operated by the drive shaft,controlling means for the high speed clutch connected with and operatedby the high speed governor, and means for locking the high speed clutchto the power shaft to render.

said clutch inactive.

35. A power transmission device comprising, in combination with a powershaft and a drive shaft, means f or hydraulically transmitting motionfrom the power shaft to the drive shaft, means for automaticallycontrolling the hydraulic fluid to control the-transmitting action forlow speeds by the R. .P. M. "of the power shaft, and means forautomatically.controlling the hydraulic fluid to connected with the lowspeed brake, a speed reduction transmission connected with saidtransmission member and the shafts, meansfor actuating the low speedbrake for transmitting moduction transmission connected with saidtransmission member and the shaft, means for actuating the low speedbrake for transmitting motion from the power shaft through saidtransmission member and said speed reduction transmission to the driveshaft at a reduced speed, said speed reduction transmission havingconnection with the high speed clutch, means for actuating the

